Turbine.



R. K. MORGOM & A. JUDE.

TURBINE. APPLICATION FILED JUNE? 13, 1908.

Patented Jan. 5, 1909.

" 2 SHEETS-SHEET 1.

Mmmsm R. K. MOROOM & A. JUDE.

TURBINE.

APPLICATION FILED JUNE 13, 1908.

Patented Jan. 5, 1909.

2 SHEETS-SHEET 2.

UNrtrED STATES PATENT OFFICE.

REGINALD KEBLE MORCOM AND ALEXANDER JUDE, OF BIRMINGHAM, ENGLAND,ASSIGNORS TO BELLISS & MOBCOM LIMITED, OF BIRMINGHAM, ENGLAND.

T'URB INE Specification 0: Letters ratent.

Patented Jan. 5,1909.

To all whom it may concern:

Be it known that we, REGINALD KEBLE MoacoM and ALEXANDER Jenn, subjectsof the King of Great Britain, residing at Led sam Street Works,Birmingham, in the county of Warwick, England, have invented new anduseful Improvements in Turbines, of which the following is aspecification.

This invention relates to an improved design of turbine to be operatedby expansive fluid in-Which, by a new combination of known elements, theenergy of high pressure steam can be renderedmechanically available in aI more economical .manner than hitherto and the invention comprisesdevices adapted to facilitate the adjustment of Y portions of theturbine sub ect to wear and tear so as to maintain, throughout theworking life of the turbine, those pressure conditions on whicheflicient action depend;

The combination referred to is that of one or more vane-carrying wheelsof relatively large diameter for the impulse'action of the fluid in theinitial or earlystages of its expansion and a drum on drums for thelater and terminalstages of the expansionfor the further impulse actionof the same fluid when,with the smaller pressure, the velocity of exitfrom the stator guide-blades less and the volume is correspondinglygreater.

Among other advantages, the impulse type of action has the merit thatthe static pressure of the fluid does not undergo any change during itspassage between any one set 0 vanes so that the displacing eiiect on therotor due to fluid-action on the vanes is derived only from the dynamicaction by virtue of which the rotor is driven. On this account the axialdisplacing force on an unpulse-driven rotor will be relatively small andpermit of the employment of a comparatively small balancing-disk ordummy-piston.

A further advantage belonging to the impulse-type of action is? thatleakage of fluid occurs only between the surface of the rotor and theinner edge of the diaphragm or partition-of the stator which carries theguideblades and not between the stator and the outer extremity of thevanes as in turbines of the pressure operating type.- Accordingly, bythe adoption of the impulseaction throughout the entire flow, theleakage areas will be minimized as well as the axial displacing force.But the adoption of the impulse-type involves a higher velocity-of vanethan would be requisite with an alternative type of action. Thisrequirement is conveniently provided for by'the-well known use of wneelsof large diameter for the initial and early stages of the expansion but,inasmuch as the employment of such wheels, in the later stages of theexpansion when the volume of the fluid to be dealt with is so muchgreater, is cumbersome and costly and causes much loss by disk-friction,we have found that with a drum-built rotorwith an increased number ofexpansion steps, to'keep down the velocity of issue from any one set ofide-blades, a much more economical ef feet will be produced.

A drum-built rotor of impulse-type will, as compared with a wheel-rotorof the same type, have a larger circumference of leakage between therotor and the inner edges of the partitions of the stator. Accordingly,to compensate for this inherent disadvantage we provide, as a portion ofthis invention, special clearance-adjusting "devices at those portionsof the turbine and as the purpose of the invention is to permanentlymaintain the necessary pressures at all parts of the turbine foreconomic andefficient working, leakageradjusting' devices will berequired at all parts where leakage. can occur as will presently bedescribed. To balance the much mitigated pre'ssure, which will be'exeerted on the rotor under the above circumstances, we adopt a revolvingidle pistondisk but, in order that one of small area and diameter maysuflice for the urpose, We

subject it to a very considerab e diil'erence of pressure on its twofaces.

1n the accompanying drawings :-.Figure 1 is a half longitudinal sectionof aturbine showing a double-wheela'nd drum combination of rotor and asingle balancing piston. Fig. 2 is a half longitudinal section of amodification in which a single wheel is combined with the drum and adiderential balancin piston is employed. Fig. 3 is a longitudindlsection of a portion of the stator and a portion of a balancing pistonor of the rotor shaft. Fig. 4 1s a ongitudinal section of a portion ofthe stator and a portion of a bal ancingpiston. Fl". 5 is a transversesection corresponding to Big. 4. Fig. 6 is a longitudinal sectionthrough a portion of the stator and of the rotor drum showing-aguide-blade'carrying partition in cross-section; Fig-.- 7 is a viewsimilar to Fig. 6 but showing a modification. Fig. 8 is a longitudinalsection of a portion of the stator and of another portion of the rotordrum, the guideblade carrying partitions being likewise shownincross-section.

Referring to Fig. 1, which is to be regarded as a representativeexdmple, a. and a. are

"of the wheel a.

wheel-portions of the rotor by means of which the steam undergoes twostages of expansion, these being fo lowed by a series'of expansionscarried out. in the drum-portions b t b of the rotor.

By adopting such conditions that the fluid, in flowing from the supplypassage. 0 to the compartment d, undergoes a fall of pressure andcorresponding acquirement of velocity-energy which is utilized in assingthe 'double, seriesof v'anes of the w eel a without furtheralteration-0f static pressure in its progress past the vanes thereof,there will be the same fluid-pressure on both sides If correspondingconditions occur in respect to the flow from the compartment d to thecompartment 6 and passage through the double series of vanes of thewheel a the pressures will be alike also on bothsides of the Wheel a.Thus by the two-foldexpansion the ressure will be very considerablyreduced wit out incurring much thrust on the rotor in an axialdirection, such thrust as occurs being due to the fluidressures on theannular areas 6 and e o the bosses of the wheels 0, and a. Additionalaxial thrust from right to left will be due to the fluid pressure on thedrum portions of the rotor, but by the combination of wheel and drumwith impulse action on both as above described, the one-way axial-forceon the rotor can be kept relatively small. To balance'this force bya-piston f of the least diameter, we sub ect one side thereof namely 9to the initial pressure of the steam by the pipe connection it and theopposite side 2 to the terminal pressure of the steam by t e pipe kwhich, when a condenser is used, W1 l be less than the atmosphericpressure.

Fig. 2 shows a modified example in which there is only one wheel a butin which there is a differential balancing piston, having two diametersf and f, the side g of which is subjected to the initialfluid-pressurecon ducted through the pipe h as before, the space 9 whichintervenes between g and g being, by the pipe 'h, subjected to anintermediate pressure which results from the expansion of the fluid fromthe supply passage 0 to the wheel a and the space g on the further sideof the larger portion of the balancing piston being subjected to a stilllower pressure which ma be the terminal pressure of the steam. In 2 thespace g 18 shown connected by a pipe l t to a space in the statorbetween the portions b and b of the rotor Where the pressure is slightlygreater than thatof the atmosphere. This will entail a somewhat largerbalancing piston than that, if leakage occurs past the stuffing box I i,it will be of steam outwards in relatively small quantity, instead ofair inwards which, by reason of a considerable difference of pressure,may be sufiicient to appreciably lmpair the vacuum. With thisarrangement also any steam which leaks past the balancing piston willbe. conducted by the pipe k to traverse the portions 5 and b of therotor and do work.

Fig. 3 shows themethod of minimizing the leakage of steam past abalancing pistonf or a portion of the rotor shaft neither of which areexposed to extreme differences of pressure, consisting of a series ofRamslottom spring-rings It each of which, onrthe operating side thereof,carries an anti-friction nonseizing substance k, such as carbon,occupying a groove formed in the side of the ring.

Figs. 4 and 5 are two .views of a contriv ance for minimizing theleakage past a balancingiston or portion of the rotor shaft expose togreater differences of pressure,

. Fig. 4 being a part-longitudinal section and art-transverse section.In these Fig. 5 a figures, t mm are, interposed between the pistonporti0n f of the rotor and the surrounding portion 0 of the stator, aplurality of rings, each composed of a plurality of segments m. Eachsement is supported by one or more stud-brfitsn, which is adapted from theoutside,even when the turbine is running, to either advance the segmenttowards the rotor or withdraw it. The steamjoint between the stator andthe back of the segments m is effected "ry flanges m which fit intointernal grooves 0 formed in the interior surface of the stator 0. 'l hejoint between the adjacent segments of each ring is effected b means ofan overlapping strip m which, be ore assembly, is secured to the end ofone segment, the end of the adjacent segment being beveled, as indicatedin dotted lines in Fig. 5, to facilitate insertion. Ihe segments mayhave a plain surface as represented by the outside rings in Fig. 4 or,as shown by the middle ring in that figure, they may he provided withdeformalle segmental packing stri s m which are adapted to yield to aradial orce and which also, by the endish shaped and thereby adapted tobe forced into closer proximity to the rotor by a deforming pressurewhich makes the angle still more obtuse. In Fig. 7 the segments p are ofY section one flange of which is adapted to be deformed, towards thesurface of the rotor. In these the principle of the, adjustment residesin the capability of fiattenlng a dished surface to a greater or lessdegree. Fig. 8 shows an adjustable mounting of the plates p of the highpressure ortion b of the rotor drum where it isdesira le that a moreexact adjustment and one also capable of being efi'ected from theexterior while the turbine is in operation, be employed. In thisconstruction the adjustment of the periphery of the plates p towards orfrom the rotor is effected in a manner similar to that adopted nuts g inFigs. 4and 5. In this figure, g g are segmental blocks by which theplates p are secured, the blocks being carried on the ends of the studbolts g g provided with looking We 0 aim: 1. A turbine for expansiblefluids comprising a wheel, vanes carried thereon, a

stator, a partition wall in said stator extend-- ing inwards to aportion of the rotor of small diameter, means for minimizing leakagebetween the edge of the partition and the rotor, guide-blades fitted inan aperture in said partition arranged to direct the fluid on to thewheel-vanes and effect an impulse-action thereon without change ofpressure while passing between the vanes, a drum, vanes carried by thedrum, a partition wall in stator extending inwards towards'the drumsurface, means for minimizing the leakage between the edge of thepartition wall and the drum surface and guide-blades fitted in anaperture in said partition arranged to direct the fluid on to thedrum-vanes and effect an impulse-action thereon without change ofpressure while passing between the vanes.

2. In a turbine, means for adjusting the clearance spaces between thestator and the 3. In a turbine, means for adjusting the the stator pclearance spaces between the stator and the periphery of abalancezpiston,compnsing segmental blocks in sai clearance spaces,

flanges on said blocks fitted in groovesv formed in the stator, stri soverlapping the butting ends of adjacent locks an adjusting bolts onwhich said blocks are mounted.

5. In aturbine, means for adjusting the clearancespaees' between thestator and the periphery of a balanceiston, comprising segmental blocksin sai clearance spaces, flanges on said blocks fitted in grooves formedin the stator, strips overlapping the butting ends ofadjacent blocks,adjustin bolts on which said blocks are mounted an deformable stripssecured to said blocks on the surface presented towards thebalancepiston.

6. In a turbine of the impulse type, means for adjustiin the clearancespaces between Iates and the low pressure portions of the rotor drum,comprising deformable segments secured to the inner borders of thestator lates.

7. In a tur me of the. impulse type, means for adjusting the clearancespaces between the stator plates and the low-pressure portions of therotor drum, comprising deformable segments'formed with an overhangingdished flange secured to the inner borders of the stator plates.

8. In a turbine of the impulse type, means for adjusting the clearancespaces between the stator plates and the high-pressure'portions of therotor drum, comprising seg mental blocks in which said plates arecarried and adjusting bolts on which said blocks are mounted.

9. In a turbine of the impulse type, means for adjusting the clearancespaces between the stator plates and the high-pressure portions of therotor-drum, comprising segmental blocks on which said plates arecarried, flanges on said blocks fitted in grooves formed in the statorand adjusting bolts on which said blocks are mounted.

In testimony whereof we have signed our names to this specification inthe presence of two subscribing witnesses.

REGINALD KEBLE MORCOM.' ,ALEXANDER JUDE.

Witnesses ERNEST BARKER, ALBERT HALSTEAD.

